Load leveling shock absorber



v- 1959 R. A. STUBBLEFIELD 3, 7

LOAD LEVELING SHOCK ABSORBER Original Filed Oct. 23, 1965 4 Sheets-Sheet1 55' 2 27 I Z .50 I.

-Z3 24 i 5 Z BY WWA NEYS J3 505 27 A. 575/55LEF/64D Nov. 4, 1969 R. A.STUBBLEFIELD 7 LOAD LEVELING SHOCK ABSORBER Original Filed Oct. 25, 19654 Sheets-Sheet 2 Nov. 4, 1969 R. A. STUBBLEFIELD 3,476,354

LOAD LEVELING SHOCK ABSORBER Original Filed Oct. 23, 1965 4 Sheets-Sheet4 5% ATTORNEYS United States Patent 3,476,354 LOAD LEVELING SHOCKABSORBER Robert A. Stubblefield, 219 F St, Salt Lake City, Utah 84103Original application Oct. 23, 1965, Ser. No. 503,036, now Patent No.3,381,952, dated May 7, 1968. Divided and this application July 6, 1967,Ser. No. 659,262

Int. Cl. F161; 31/143, 31/383; B60g 11/26 US. Cl. 25163 2 ClaimsABSTRACT OF THE DISCLOSURE A load leveling shock absorber unit includinga first piston and cylinder, one of which is connected to a sprung massand the other of which is connected to an unsprung mass, and a secondpiston and cylinder, the piston of which is connected to one of themasses through a spring and the cylinder of which is connected directlyto the other of the masses. These cylinders are concentrically arrangedand are of the hydraulic type. The first piston reciprocates within thefirst cylinder in accordance with undulations in a road surface or thelike. If the first piston is located within a mid-portion of the firstcylinder such reciprocatory movement has no effect on the second piston.However if such reciprocation of the first piston occurs at either ofthe opposite end positions of the first cylinder it has the effect ofpumping fluid through a valve element and into or out of the secondcylinder below the second piston to raise or lower the second piston inthe second cylinder and thus raise or lower the sprung mass relative tothe unsprung mass. The valve element includes a valve cylinder having apair of ports communicating with the first and second cylinders. A valvemember is slidably carried in the valve cylinder and is movable betweena first position at which said valve member blocks the ports to a secondposition at which the valve member opens the ports. A spring biases thevalve member to the first position thereof and a motive surface isformed on the valve member for receiving a force acting against thespring to move the valve member to the second position thereof.

CROSS-REFERENCES TO RELATED APPLICATION This application is a divisionof my parent application Ser. No. 503,036, filed Oct. 23, 1965, nowPatent No. 3,381,952.

SUMMARY OF THE INVENTION This invention relates generally to vehicularshock absorber units and more particularly to an absorber unit whichcompensates itself for variations in vehicular loading to maintain agiven level of the sprung mass of the vehicle.

An object of this invention is to provide a load-leveling shock absorberunit which is dependable in operation over extensive periods of use.Known devices of this type are generally complicated and thereforesusceptible to many mechanical difficulties, with the expense in repairand replacement attendant thereto. Furthermore, when replacement isnecessary the period of down time of the vehicle can be inconvenient andresult in additional expense or loss. By contrast, the present inventionis embodied in a device which is simple in design and construction andincludes a minimal number of moving and closely machined parts.

Another object of the invention is to provide a loadleveling absorberunit which is relatively inexpensive in manufacture. Many vehicularaccessories and improveice ments achieve little or no commercial successregardless of improved comfort, safety, performance, etc., derivabletherefrom simply because the increased cost is prohibitive. Thus in theautomotive field manufacturers are apparently reluctant to includeload-levelers as standard equipment on all models because of therelatively substantial costs involved. The cost of manufacture of theload leveler of the present invention, however, has been appreciablyreduced in order to make available the advantages of load levelers tomany more uses of automotive vehicles.

Still another object of the present invention is to eliminate therequirement of an external power source, and also to eliminate thenecessity for gas pressure chambers, sundry diaphragms, bladders and thelike found in some load levelers.

The shock absorber unit of this invention can be utilized either aloneor in combination with the shock absorbers of a conventional suspensionsystem, since the upper frame of the vehicle is not merely maintained ata given level but is also supported by the shock absorber unit.

Basically, the present invention comprises a first piston and cylinder,one of which is connected to the sprung mass and the other of which isconnected to the unsprung mass, and a second piston and cylinder, thepiston being connected to one of the masses through a spring and thecylinder being connected to the other of the masses.

The invention is hydraulically operated, and the two cylinders are influid communication with one another. When the vehicle is loaded with anaverage weight the first piston is situated in the central portion ofthe first cylinder and undulations in the road surface as the vehiclemoves thereacross have the effect of causing the first piston toreciprocate back and forth within the central portion of the firstcylinder with no effect on the second piston.

When an extra load is added to the vehicle the first piston moves downinto the lower portion of the first cylinder. Reciprocal movement of thefirst piston within the lower portion of the first cylinder, caused byan uneven road surface, has the effect of pumping hydraulic fluid fromthe first cylinder into the second cylinder, thereby raising the secondpiston and the spring, and thus the sprung mass of the vehicle. Suchraising continues until the sprung mass has been raised sufliciently sothat the first piston again resides within the central portion of thefirst cylinder, whereupon further reciprocation of the first piston hasno further effect in raising the sprung mass.

If the load is subsequently reduced to below an average, the firstpiston is urged upwardly by the spring into the upper portion of thefirst cylinder. Reciprocal movement of the first piston in that positionthereof has the effect of withdrawing the fluid from the secondcylinder, thereby lowering the second piston and the spring and, as aresult, the sprung mass of the vehicle. Lowering of the sprung mass hasthe effect of lowering the position of the first piston in the firstcylinder until it again resides within the central portion of the firstcylinder. Subsequent reciprocal movement of the first piston when it iswithin the central portion of the first cylinder has no further effectin lowering the sprung mass.

The flow of fluid between the two cylinders is controlled by variousvalving arrangements that are actuated by the movement of the firstpiston. The device is completely self-contained and requires no externalpower source for actuation of the piston or valve structures.

Many other features, advantages and additional objects of the presentinvention will become manifest to those versed in the art upon makingreference to the detailed description which follows and the accompanyingsheets of drawings, in which preferred structural embodimentsincorporating the principles of the present invention are shown by wayof illustrative example only.

BRIEF DESCRIPTION OF THE DRAWING FIGURE 1 is an elevational view of anexemplary embodiment of a load-leveling shock absorber unit constructedin accordance with the principles of the present invention;

FIGURE 2 is a vertical sectional view of the absorber unit of FIGURE 1taken through a plane intersecting the longitudinal axis of the unit;

FIGURE 3 is a fragmentary vertical sectional view similar to FIGURE 2but taken through a plane offset angularly with respect to the plane ofFIGURE 2;

FIGURES 4 and 5 are also similar to FIGURE 2 but taken through otherplanes oifset with respect to the planes of FIGURES 2 and 3;

FIGURE 6 is a horizontal sectional view taken along lines VI-VI ofFIGURE 2;

FIGURE 7 is a horizontal sectional view taken along lines VIIVII ofFIGURE 2;

FIGURE 8 is an enlarged fragmentary sectional view emphasizing anexemplary valve arrangement of the invention;

FIGURE 9 is a vertical sectional view of another embodiment of theinvention taken through a plane intersecting the longitudinal axis ofthe unit; and

FIGURE 10 is a vertical sectional view similar to FIG- URE 9 but takenthrough a plane offset with respect to a plane of FIGURE 9.

DESCRIPTION OF THE PREFERRED EMBODIMENTS In FIGURE 1 reference character20- indicates generally a load-leveling shock absorber unit constructedin accordance with the principles of the present invention andcomprising an outer cylindrical casing 21 having formed thereon at oneend thereof a connector flange 22. A plurality of piston rods 23, 24,and 26 project upwardly from the casing 21 and are joined in fixedassembly at the top thereof by means of a companion connector flange 27.The connector flanges 22 and 27 are adapted for connection to the sprungand unsprung masses of a vehicle and are apertured as at 28 for thatpurpose.

As shown in FIGURE 2 the outer casing 21 is closed at the lower endthereof by a base plate 29 and at the top end thereof by an end cap 30.A concentric cylinder wall 31 which has a diameter substantially lessthan the diameter of the casing 21 interconnects the base plate 29 andthe end cap 30 in fixed assembly.

A transverse plug or insert 32 is securely mounted within the cylinderwall 31 downwardly from the end cap 30 to partition the cylinder 33formed by the cylindrical wall 31 into two separated portions.

Another concentric cylinder wall 34 having a diameter which is slightlyless than the diameter of the cylinder wall 31 extends from the plug 32to the base plate 29 whereby a tubularly shaped space is providedbetween cylinder walls 31 and 34. A plurality of axially extendinggrooves 36, 37 and 38 are formed in the cylinder wall 34 and terminaterespectively at an upper end 39 situated below the end cap 30, and at alower end 40 situated above the base plate 29. A plurality of axiallyextending tubularly shaped circumferentially spaced sleeve members 41,42 and 43 are housed in the space between cylindrical walls 31 and 34 toprovide a plurality of axially extending fluid passages 44, 46 and 47.

The piston rods 23, 24 and 26 extend through bores 48, 49 and 50 formedin the end cap 30 and are surrounded by sealing members 51-53 to protectleakage of fluid past the end cap 30. The center piston rod 23 alsoextends through a bore 54 formed in the plug 32 and has mounted at thelower end thereof within a cylinder 56 formed by the cylinder wall 34 apiston 57 carrying a circumferential sealing ring 58. The other twopiston rods 24 and 26 have mounted thereon at the lOwer ends thereof inthe annular space between the casing 21 and the cylinder wall 31, saidannular space being referred to hereinafter as a cylinder 59, an annularring 60 having a plurality of passages at 61 formed therein andextending axially therethrough.

Situated underneath and supporting the ring 60 is a heavy helical coilspring 62 which is wound within the cylinder 59 and which is, in turn,supported by a piston member 63 situated at the lower end portion of thecylinder 59. In order to prevent leakage of fluid past the piston 63 aplurality of sealing members such as O-rings 64, 66 and 67 are mountedthereon in sealing contact with both the inside surface of the casing 21and the outside surface of the cylinder wall 31.

Before the absorber unit 20 is completely assembled the cylinder 59 issubstantially filled with fluid such as oil to a level indicated at F.As a result of the passages 61 formed in the ring 60 the fluid fills thecylinder 59 below the ring 60, and as a result of a plurality ofregistered bores 68 and 69 formed respectively in the cylinder wall 31and the sleeves 41-43 at the upper ends 39 of the grooves 36-38, thecylinder 56 is also filled with fluid both above and "below the piston57. The cylinder 59 has no fluid in it below the piston 63 at this pointin time, and as a result piston 63 is bottomed on an inner wall 70 ofthe base plate 29.

The k" factor of the spring 62 is such that when a plu rality ofabsorber units 20 are mounted on a vehicle having an average loadthereon between the sprung and the unsprung masses, either by themselvesor in combination with conventional absorbert devices, the ring 60 ismaintained by the spring 62 in spaced relation to the piston 63, whichis bottomed on the base plate 29, such that the piston 57 resides withinthe central portion of the cylinder 56, that is, that portion of thecylinder 56 which extends axially between the ends 39 and 40 of thegrooves 3638. When the vehicle is in motion irregularities in the roadsurface causes the piston rod 23, 24 and 26 and the piston 57 and thering 60 to oscillate or reciprocate Within cylinders 56 and 59. Thisoscillatory movement of piston 57 within the central portion of thecylinder 56 has no pumping effect on the fluid within cylinder 56 sincethe fluid is merely moved back and forth from one side of the piston 57to the other side through the grooves 3638.

Assume, however, that an extra load is applied to the sprung mass of thevehicle. In such event the spring 62 is compressed accordingly, whichresults in the movement of ring 60 downwardly. Piston 57 also movesdownwardly such that it then resides within a lower portion of cylinder56, that is, that portion thereof which extends axially from the bottoms40 of the grooves 36-38 to the top wall 70 of the base plate 29.

Oscillations of the piston 57 when it is within this lower portion ofthe cylinder 56 does have a pumping effect on the fluid to raise theunsprung mass. Referring to FIG- URE 3, as the piston 57 movesdownwardly, the fluid in cylinder 56 below the piston 57, in an amountproportinate to the travel of the piston 57, is forced through a pair ofpassages 71 and 72 formed in the base plate 29 which communicate thelower end of cylinder 56 with the lower end of cylinder 59 through apair of check valves 73 and 74 which open into cylinder 59 through theinner wall 70 of the base plate 29. The piston 63 is raised accordingly,thereby raising slightly the spring 62, the ring 60 which it supports,the sprung mass of the vehicle and, in addition, the piston 57 incylinder 56. During a subsequent upward movement of the piston 57 (stillwhile within the lower portion of the cylinder 56) fluid is supplied tocylinder 56 below the piston 57 from cylinder 59, but from a point abovethe piston 63, Referring now to FIG- URE 5, it will be noted that asmall aperture 76 is formed in the cylinder wall 34 adjacent the baseplate 29, which aperture 76 communicates the lower portion of cylinder56 with passage 44. At the upper end of passage 44 an aperture 77 isformed in the cylinder wall 31, thereby communicating passage 44 withthe cylinder 59. A check valve 78 is mounted within the passage 44 toenable fluid to flow from cylinder 59 through passage 44 to the lowerportion of cylinder 56 as piston 57 moves upwardly in cylinder 56 withinthe lower portion thereof.

Thus it will be noted that when piston 57 is situated within the lowerportion of cylinder 56, for each downward motion of the piston 57,piston 63 is raised slightly to raise the sprung mass of the vehicle aswell as to raise the position of piston 57 within cylinder 56. As piston57 moves upwardly fluid fills the void below it as it is drawn throughaperture 76 from the passage 44 and the cylinder 59.

The piston 57 will ultimatel rise to again reside within the centralportion of cylinder 56 and further undulations in the road surface willhave no eiTect in raising or lowering the sprung mass of the vehicle.

Assume now that the extra load is removed from the vehicle. The spring62 expands to urge the ring 60 upwardly, thereby moving the piston 57into the upper portion of the cylinder 56, that is, that portion thereofbetween the upper ends 39 of grooves 3638 and the plug 32.

Irregularities in the surface of the road will cause the piston 57 tooscillate in the upper portion of the cylinder 56. An upward movement ofthe piston 57 has the effect of pumping fluid from the top of the piston57 through an aperture 79 formed in the cylinder wall 34 adjacent theplug 32, and downwardly through passage 46 past a check valve 80 mountedwithin passage 46.

As is shown in FIGURE 2, a bore 81 is formed in the base plate 29 inregister with the passage 46 and communicates with a cylindrical bore 82also formed in the base plate 29 and extending transversely to thelongitudinal axis of the unit 20.

The cylinder 82 houses a foot valve indicated generally at referencenumeral 83 which comprises a valve mem ber 84 urged toward an end wall87 of the cylinder 82 by means of a spring 88. The valve member 84 istapered slightly at one end 89 thereof but an opposite end 90 thereof iscylindrical and has a diameter slightly less than the diameter of thecylinder 82.

As the fluid is pumped downwardly through passage 46 and the bore 81into the cylinder 82, the valve member 84 is urged rightwardly as viewedin FIGURE 2 until an annular circumferential groove 91 formed in theperipheral surface of end 90 of the valve member 84 is aligned with acomplemental annular groove 92 formed in the base plate 29 andcommunicating with a passage 93 opening to the cylinder 56 through thewall 70 of the base plate 29.

When grooves 91 and 92 are aligned a fluid flow path is opened betweencylinder 59 below piston 63 and the lower portion of 56 through a pairof passages 93 and 94 (FIGURES 2 and 3) which communicate cylinder 59with the groove 92. As a result some of the fluid in cylinder 59 belowthe piston 63 flows into the cylinder 56, thereby lowering the piston 63and, correspondingly, the spring 62, the ring 60, the sprung mass of thevehicle and the piston 57 in cylinder 56. Some of the fluid which enterscylinder 82 through the passage 46 and the bore 81 enters the cylinder56 through another bore 96 formed in the base plate 29, and theremainder of the fluid enters cylinder 56 by leaking past the valvemember and into the groove 92 to pass through the bore 93 into thecylinder 56.

As the piston 57 moves downwardly in the upper portion of cylinder 56the excess fluid in cylinder 56 below piston 57 can escape through ports68 and 69 into the cylinder 59. The void above piston 57, however, issupplied with fluid through the longitudinal passage 47 which is incommunication with a portion 97 of the cylinder 82 which houses thespring 88 through a passageway 98 (FIGURES 2, 4 and 6) formed in thebase plate 29. The upper end of passage 47 (FIGURE 4) is incommunication with the upper end of cylinder 56 through *6 an aperture99 formed in the cylinder wall 34. A check valve 100 is housed withinpassage 47 to preclude reverse flow of the fluid therethrough.

Accordingly, each oscillation of the position 57 when it is situatedwithin the upper region or portion of the cylinder 56 has the effect ofwithdrawing fluid from the cylinder 59 below piston 63 into the cylinder56 below piston 57. The piston 63 moves incrementally toward the wall 70of the base plate 29, thereby lowering the spring 62, the ring 60' andthe sprung mass of the vehicle until the piston 57 again resides withinthe central portion of the cylinder 56.

Another embodiment of the invention is shown in FIG- URES 9 and 10,wherein parts similar in function to those shown in FIGURES 18 are giventhe same reference numerals raised by 100. In this embodiment the spring162 is not supported directly by the piston 163, but instead is bottomedas at 200 on an annular bracket 201 which surrounds the casing 121 inradially spaced relation. A top end 202 of the spring 162 directlysupports the connector member 127 and thus the sprung mass of thevehicle.

Rods 124 and 126 are fixedly connected at opposite ends to the piston163 and the ring 160, and the ring in turn is connected in fixedassembly to the annular bracket 201 by means of an external tubularsleeve 203 which telescopes over the casing 121.

Unlike the embodiment illustrated in FIGURES l-8, there are no sleevemembers between the outer cylinder wall 131 and the inner cylinder wall134. A series of circumferentially spaced apertures are formed in thecylinder wall 134 for communicating the cylinder 156 with the spacebetween cylinder walls 131 and 134. Another series of apertures 206 areformed in cylinder wall 134 in axially spaced relation to apertures 204and the longitudinal extent of cylinder 156 between apertures 204 andapertures 206 constitutes the central portion of cylinder 156, thatportion thereof between apertures 204 and wall of the base plate 129constituting the lower portion of the cylinder, and that portion betweenapertures 206 and the end cap 130 constituting the upper portion ofcylinder 156.

In addition a plurality of circumferentially spaced apertures 207 areformed in the cylinder wall 131 in order to communicate the spacebetween cylinder walls 131 and 134 with the cylinder 159.

When the absorber unit 120 is subjected to an average load, the piston157 resides within the central portion of cylinder 156. When an extraload is applied the piston 157 will move downwardly as viewed in FIGURE10 to the lower portion of cylinder 156, thereby pumping fluid from thelower portion of cylinder 156 through passages 171 and 172 formed in thebase plates 129 into the cylinder 159 below the piston 163. This raisesthe piston 163 which in turn raises the annular bracket 201, the spring162 and also the unsprung mass of the vehicle. Subsequent oscillationsof the piston 157 while it is within the lower portion of cylinder 156will have the eflect of continuing to raise the unsprung mass of thevehicle until the piston 157 resides again within the central portion ofcylinder 156, whereupon oscillations of piston 157 will have no furthereffect upon the raising of the vehicle.

It should be noted that when the piston 157 is situated within the lowerportion of cylinder 156 and is rising within that cylinder, the voidbelow piston 157 is filled by leakage past the piston rather than by apassage similar to passage 44 in the embodiment of FIGURES 18. Sucharrangement has the salutory effect of somewhat dampening theoscillations of the piston 157, which may be desirable in certainapplications of the absorber unit 120.

When the extra load is removed from the unit 120, the piston 157 tendsto rise above apertures 207 into the upper portion of cylinder 156. Thishas the effect of moving a washer or disc slidably carried in cylinder156 in surrounding relation to the rod 123 upwardly toward the end cap130. As best seen in FIGURE 9, the washer 208 is fixedly connected to awire-like rod 209 which extends axially in the space between cylinderwalls 131 and 134 down into the base plate 129'. An inturned upper end210 of the rod 209 extends through an aperture 211 formed in the upperend of cylinder Wall 134, and the washer or disc 208 normally covers orcloses the aperture 211.

A lower end 212 of the rod 209 is connected to a pin 213 which pivotallyconnects a pair of linkage members 214 and 216. As rod 209 is movedupwardly by the disc 208 when the piston 157 moves upwardly in the upperend portion of cylinder 156, thereby pressurizing the fluid to move thewasher 208 upwardly, it has the effect of opening up or increasing theangle between the linkage member 214, an upwardly sloping end 217 ofwhich abuts a plug 218 in the cylinder 182, and the linkage member 216,an upwardly sloping end of which abuts the valve member 184 in thecylinder 182.

As a result, the valve member 184 is mechanically (as opposed tohydraulically) moved rightwardly as viewed in FIGURE 9 whereupon thecircumferential groove 191 thereof is brought into alignment with thegroove 192 formed in the base plate 129 to communicate cylinder 159below piston 163 with cylinder 156 below piston 157 through a passage193.

It will thus be appreciated that upward movement of piston 157 in theupper portion of cylinder 156 has the effect of withdrawing fluid fromcylinder 159 and discharging it into cylinder 156 whereupon the unsprungmass of the vehicle is incrementally lowered. When the piston 157 movesdownwardly in the upper portion of cylinder 156, once again the voidabove the piston 157 is filled, in the embodiment of FIGURES 9 and 10,by leakage of the fluid past the piston 157.

In both of the illustrated embodiments of the invention, that is, theembodiment illustrated in FIGURES 1-8 and the other embodimentillustrated in FIGURES 9 and 10, a narrow diameter passageway 217 isformed in the valve member (84, 184) and communicates thecircumferential groove (91, 191) formed in the valve member with thatportion of the cylinder (82, 182) in which the spring (88, 188) ishoused. The purpose of passageway 217 is to enable the fluid in thecylinder (82, 182) behind the valve member (84, 184) to escape when thevalve member is urged rightwardly as viewed, for example, in FIGURES 2and 9. In addition fluid can move back into this portion of the cylinderwhen the valve member is urged leftwardly by the spring (88, 188). Whilethe invention is operative without the passageway 217 in the valvemember (84, 184) the invention is not as quick to respond in maintaininga given level of the vehicle upon variations in loading, since then thefluid must leak past the valve member (84, 184) to and from that portion(97, 197) of the cylinder (82, 182) in which the spring (88, 188) ishoused.

I claim as my invention:

1. In a load leveling shock absorber having a pair of concentriccylinders and a base plate closing the cylinders at one of the endsthereof, a valve assembly for connecting the cylinders in fluidcommunication comprising means forming a valve cylinder in said baseplate,

means forming a pair of ports in the Wall of said valve cylindercommunicating respectively said valve cylinder and one of saidconcentric cylinders and said valve cylinder and the other of saidconcentric cylinders,

a complemental valve member slidably carried in said valve cylinderhaving a pair of radial motive surfaces formed thereon at opposite endsthereof, a circumferential groove formed in said valve member betweensaid motive surfaces,

biasing means in said valve cylinder on one side of said valve memberacting on one of said motive surfaces for biasing said valve member to afirst position whereat said valve member blocks said ports, means actingon the other of said motive surfaces for moving said valve memberagainst said biasing means to a second position whereat said groovecommunicates said ports to provide a flow path between said concentriccylinders, and

a bore formed in said valve member and opening at opposite ends thereofinto said groove and said one of said motive surfaces to provide a flowpath between said groove and said valve cylinder on said one side ofsaid valve member.

2. In a load leveling shock absorber having a pair of concentriccylinders and a base plate closing the cylinders at one end, a valveassembly for connecting the cylinders in fluid communication comprisingmeans forming a valve cylinder in said base plate, means forming a pairof ports in the wall of said valve cylinder communicating said valvecylinder and said concentric cylinders,

a complemental valve member having a cylindrical portion and a radiallyinwardly tapered portion slidably carried in said valve cylinder andhaving a pair of radial motive surfaces formed thereon at opposite endsthereof, a circumferential groove formed in said cylindrical portion ofsaid valve member,

biasing means in said valve cylinder on one side of said valve memberacting on one of said motive surfaces for biasing said valve member to afirst position at which said valve member blocks said ports, and meansacting on the other of said motive surfaces for moving said valve memberagainst said biasing means to a second position at which said groovecommunicates said ports to provide a flow path between said concentriccylinders.

References Cited UNITED STATES PATENTS 787,705 4/ 1905 Templin 251-632,020,773 11/1935 Ernst 25163 2,23 7,915 4/1941 Routson 267-34 3,145,0558/1964 Carter 267-34 X ARNOLD ROSENTHAL, Primary Examiner U.S. Cl. X.R.267-34, 64

